US5375464A - Process for device for steering vehicle wheels rolling on test stands - Google Patents

Process for device for steering vehicle wheels rolling on test stands Download PDF

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Publication number
US5375464A
US5375464A US08/037,327 US3732793A US5375464A US 5375464 A US5375464 A US 5375464A US 3732793 A US3732793 A US 3732793A US 5375464 A US5375464 A US 5375464A
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US
United States
Prior art keywords
vehicle
steering
chassis
test stand
wheels
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US08/037,327
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English (en)
Inventor
Hans J. Dadt
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Carl Schenck AG
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Carl Schenck AG
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Assigned to CARL SCHENCK AG reassignment CARL SCHENCK AG ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: DADT, HANS JOACHIM
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Publication of US5375464A publication Critical patent/US5375464A/en
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M17/00—Testing of vehicles
    • G01M17/007—Wheeled or endless-tracked vehicles
    • G01M17/04—Suspension or damping
    • G01M17/045—Suspension or damping the vehicle wheels co-operating with rotatable rollers
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M17/00—Testing of vehicles
    • G01M17/007—Wheeled or endless-tracked vehicles
    • G01M17/0072—Wheeled or endless-tracked vehicles the wheels of the vehicle co-operating with rotatable rolls
    • G01M17/0074—Details, e.g. roller construction, vehicle restraining devices
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M17/00—Testing of vehicles
    • G01M17/007—Wheeled or endless-tracked vehicles
    • G01M17/06—Steering behaviour; Rolling behaviour
    • G01M17/065—Steering behaviour; Rolling behaviour the vehicle wheels co-operating with rotatable rolls

Definitions

  • the present invention relates to a process and device for steering vehicle wheels rolling on test stands in order to determine vehicle behavior under actual operating conditions.
  • vehicle test stands serve to examine, for example, the braking behavior of vehicles during the development and production stages.
  • test stands which can be designed with flat belt units or running drums, are used to measure the camber and track of the vehicle and also to test the behavior of the vehicle during actual operation.
  • these test stands are used to apply parameters previously ascertained on test runs, for example, pertaining to the spring deflection and swaying or shaking of a vehicle on the drive unit of the flat belt or drum-type test stand, in order to use the test stand to examine selected operating conditions of vehicles that have already been completed. Then, on the basis of these test results, the vehicles can be improved with respect to the anticipated conditions.
  • test stands where either only the steered axle of the vehicle or only the non-steered axle of the vehicle is in contact with a test stand. In this process, the vehicle can be driven on the test stand via the steered wheels or else via the non-steered wheels.
  • a familiar passive system consists in holding the steering wheel in an articulated manner by means of a rod or the like arranged perpendicular to the vehicle on a fixed point of the building or of the foundations so that the vehicle steers itself when it is moved, but only when no significant vertical forces occur in the test stand.
  • swaying refers to a rolling motion of the vehicle by the length of one vehicle axis which, depending on the particular spring deflection of the vehicle wheels, generally moves away from its zero position.
  • the rigid articulated rod leads to unnecessary motions of the steering wheel, a shifting of the vehicle away from its zero position and also to unstable steering. If the lateral shifting is prevented, for example, by a lateral anchoring or strapping of the vehicle, then inevitably constraining forces are exerted on the vehicle which can interfere with the test results.
  • the present invention is based on the task of obtaining measured results on the riding comfort which, in addition to the swaying and shaking motions of the vehicle, also includes the avoidance of driving noises in the interior of the car. Also, results are obtained from studies on the noise coming through openings in the closed vehicle such as the trunk lid and the hood when the vehicle is subjected to great vertical forces. This is accomplished without the need for lateral anchoring of the vehicle which would affect the measured results. Moreover, the swaying components which occur in response to great vertical motions do not initiate any additional steering movements.
  • the steering point on the vehicle is spatially separated with respect to the measuring point for determining the excursion of the vehicle.
  • the steering is influenced only in such a way that overcompensation, which would lead to erroneous measurements, does not occur. Also, errors due to the anchoring of the vehicle cannot occur either.
  • pretensioning is allowed to be exerted on the steering plane in the case of transmitting means which must be pretensioned and which only transmit forces in one direction.
  • transmitting means which must be pretensioned and which only transmit forces in one direction.
  • a device of the present invention measures the lateral motion of a part of the vehicle via at least one sensor with respect to a fixed point.
  • the steerable wheels are steered from a steering point, practically excluding the swaying component only as a function of the lateral motion from the distance difference of the vehicle.
  • the vehicle is prevented from breaking away from the test stand or from flying away from the test stand, without the need for an additional lateral anchoring of the vehicle. Such anchoring would interfere with the measured values and, at the same time, would interfere with a vehicle adjusted in accordance with these values, thus rendering the adjustment of a vehicle non-reproducible.
  • a rope connects the reference point via deflection elements with an adjustable radius of the steering wheel of the vehicle to be tested and with which device the adjustable radius of the steering wheel is connected via a spring which provides the pretensioning to a place on the moving vehicle.
  • the spring which provides the pretensioning for the rope does not have to lie on the same plane as the rope but rather can be located by means of appropriate deflection elements at any place inside or outside of the passenger compartment of the moving vehicle.
  • Another embodiment uses a hydraulic mechanism consisting of a hydraulic cylinder and a hydraulic piston rod positioned between the reference point and a measuring point on the vehicle's chassis.
  • a hydraulic mechanism consisting of a hydraulic cylinder and a hydraulic piston rod positioned between the reference point and a measuring point on the vehicle's chassis.
  • information about the lateral motion is transmitted to a second hydraulic cylinder via hydraulic medium and via hoses.
  • the second hydraulic cylinder rests on the vehicle and is connected to its steering wheel with an adjustable radius.
  • the piston rod of the second hydraulic cylinder which is connected in an articulated manner with a point of an adjustable radius of the steering wheel, is then used to turn the steering wheel in response to the lateral motions, considering the swaying motion to be practically negligible, and thus to effectuate a steering correction on the test stand.
  • an electric signal is transmitted to a control device depending on the distance change and this control signal is transmitted to an actuation device.
  • the actuation device is preferably positioned in an articulated manner inside the passenger compartment of the vehicle and it interacts with an adjustable radius of the steering wheel with which it is connected in an articulated manner. As a result, corrective steering movements can be transmitted to the steered wheels in an active way.
  • At least one sensor is shifted with respect to the steering point.
  • FIG. 1 is a front elevational view of a device for the passive steering of a vehicle subjected to great vertical forces, the steering wheel being connected to a stationary reference point outside of the vehicle, according to the present invention
  • FIG. 2 is a front elevational view of another device for the passive steering of a vehicle, according to the present invention.
  • FIG. 3 is a front elevational view of still another device for the passive steering of a vehicle, according to the present invention.
  • FIG. 4 is a front elevational view of a device for the active steering of a vehicle, according to the present invention.
  • FIG. 1 shows a vehicle 1 rolling with its steered wheels 2 on a test stand 3. It does not matter whether the test stand 3 is a drum-type test stand or a flat belt test stand, as is shown in FIG. 1. Likewise, it does not matter whether the rolling steered wheels 2 are driven by the vehicle 1 or are driven by the test stand 3, or whether the test stand 3 and the vehicle 1 are both driving the wheels at the same time.
  • the test stand 3 is supported on a device 4 and on another device 5 which are designed to exert vertical forces.
  • Double arrows 6 illustrate that the device 4 and the additional device 5 can exert vertical forces independently of each other, so that, for example, the flat belt test stands 3 may transmit vertical forces of different strengths onto the steered wheels 2.
  • the frequency of the vertical force between the device 4 and the additional device 5 can also be different in magnitude so that, in addition to an inclined positioning of the vehicle 1, the different force frequencies also have an effect which influences the steering of the vehicle 1 and thus will lead to a steering correction which manifests itself at the steering wheel 7.
  • the steering wheel 7 it is also possible to use the steered wheels 2 or else the steering rods (not shown here), for example, the gauge rod of the vehicle, as the point of application for the steering correction which is brought about, as described above.
  • the rod arrangement 9 consisting of a rod 10 which is horizontal in its basic position, i.e. in the middle position of the vertical force, and of a deflection element 8, only the lateral motions and not the rotational components, are transmitted by sensing chassis 11 during the swaying of the vehicle 1 when the horizontal rod 10 is located at the height of the swaying axis 13 when the vehicle 1 is not swaying. Consequently, this achieves that the end point of the rod be on the chassis side carries out practically no lateral motion during the swaying of the vehicle.
  • the other end of the rod 10 is attached in an articulated manner to a fixed point of the building or of the test stand and thus serves as a stationary reference point 16.
  • the deflection element 8 transmits the lateral motion of the vehicle determined with respect to the end of the rod 10 on the chassis side via a rigid connection rod 12, which is connected in an articulated manner, to another deflection element 8A attached to the vehicle and to a rigid steering rod 14 which is likewise connected in an articulated manner to the steering wheel 7.
  • the steering rod 14 is connected in an articulated manner to an adjustable radius of the steering wheel 7.
  • the adjustable radius consists of a rod of any length attached to the turning point of the steering wheel and to the periphery of the steering wheel.
  • this rod can also extend beyond the steering wheel.
  • the lever ratios of the deflection elements 8 and 8A are likewise adjustable. As a result, the amplification of the rod arrangement 9 can be adapted to the gearing of the steering mechanism of the vehicle.
  • Passive steering refers to the rod arrangement 9 by means of which the vehicle 1 is steered via the steering wheel 7 without additionally imparted energy.
  • active steering refers to the steering of the vehicle 1 with additionally imparted energy.
  • the vehicle is steered as a function of the vehicle's lateral motions that occur, but practically without influences by swaying motions.
  • This passive steering by means of which the rotational component is practically compensated for when the vehicle sways, also makes it possible to reliably steer the vehicle to be tested on the narrow flat belt merely by passive steering.
  • FIG. 2 The embodiment of a passive steering system with sway compensation is illustrated in FIG. 2.
  • the vehicle 1 is positioned with its steered wheels 2 on the flat belts of the vehicle test stand.
  • the flat belts are moved in a vertical direction 6 by the device 4 and the additional device 5.
  • the reference point 16 is connected with a radius of the steering wheel 7 via a rope 17 by means of a lower deflection roller 18 and an upper deflection roller 19.
  • the rope 17 is a means with which the force can be transmitted in just one direction. Only during the pretensioning can the force be exerted in two directions.
  • the lower deflection roller 18 serves at the same time as the measuring point 15 for determining the lateral excursion of the vehicle.
  • the lower deflection roller 18 and the upper deflection roller 19 are attached to the vehicle 1 in such a way that they can be removed, but the lower deflection roller 18 is attached at the height of the swaying axis 13 of the vehicle 1 in such a way that the rope 17 runs in a horizontal direction between the measuring point 15 and the reference point 16 when the vehicle is in its basic position.
  • a spring 20 consisting of metal, non-metal, plastic or the like functions as a pretensioning mechanism.
  • the spring is attached to the vehicle 1 at a point 21 and on the steering wheel 7 at a radius. It has the effect that the rope 17 can transmit forces in both directions.
  • the point 21 does not have to be located at the place shown in FIG. 2, but rather can be at any place inside the vehicle, as long as care is taken that the direction of effect of the spring 20 is on one plane with the adjustable radius.
  • the amplification of the steering device can be adapted to the gearing of the vehicle's steering mechanism.
  • FIG. 3 The embodiment of another passive steering system with sway compensation is illustrated in FIG. 3.
  • the vehicle 1 is positioned with its steered wheels 2 on the flat belts 3 of the vehicle test stand.
  • the flat belts are moved in a vertical direction 6 by the devices 4 and 5.
  • the reference point 16 is connected to the measuring point 15 of the vehicle via a horizontally arranged hydraulic cylinder and piston rod 22.
  • the cylinder and piston lie at the height of the swaying axis 13.
  • This hydraulic cylinder and piston rod 22 are connected via hydraulic hoses 23 to another hydraulic cylinder with another piston rod 24.
  • This piston rod engages an adjustable radius of the steering wheel 7. Due to the lateral motion of the measuring point 15, a hydraulic medium is now displaced in the hydraulic cylinder with the actuation rod 22 and made to flow via the hoses 23 into the additional hydraulic cylinder with the additional piston rod 24.
  • This piston rod transmits the lateral motion of the measuring point 15 as a steering correction to the adjustable radius of the steering wheel 7.
  • the adjustable radius of the steering wheel 7 represents the adaptation of the amplification.
  • the advantage of this device is that it can be operated by means of thin hoses 23 which can pass through the door seal of the vehicle 1 when the door is closed. As a result, tests can be carried out while the doors and windows of the vehicle are closed.
  • FIG. 4 shows the vehicle 1 standing with its steered wheels 2 on the vehicle test stand with flat belts 3. The belts are moved in a vertical direction 6 by the device 4 and the additional device 5.
  • the reference point 16 is connected to the measuring point 15 of the vehicle via a horizontally positioned position sensor 25.
  • This position sensor 25 preferably lies at the height of the swaying axis 13.
  • the position sensor can preferably be an inductive, a resistance or a non-contact measuring device, which uses light, for example.
  • the position sensor 25 reports the lateral excursion of the measuring point 15 of the vehicle to a control unit 26.
  • This unit evaluates the signal and transmits a steering correction to the active control element 27.
  • This active control element 27 rests on one side of the vehicle and on the other side on an adjustable radius of the steering wheel 7 thereby transmitting the steering correction to the steering wheel 7.
  • the active control element 27 is preferably designed as an electric element such as, for example, an electric spindle, but other designs with regulated pneumatic and hydraulic cylinders are also possible. With this version of the steering device, tests are also possible while the doors and windows of the vehicle 1 are closed.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Vehicle Body Suspensions (AREA)
  • Automobile Manufacture Line, Endless Track Vehicle, Trailer (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
US08/037,327 1992-05-29 1993-03-26 Process for device for steering vehicle wheels rolling on test stands Expired - Fee Related US5375464A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP92109007A EP0577855B1 (de) 1992-05-29 1992-05-29 Verfahren und Vorrichtung zur Lenkung abrollender Räder eines Fahrzeugs auf Prüfständen
EP92109007 1992-05-29

Publications (1)

Publication Number Publication Date
US5375464A true US5375464A (en) 1994-12-27

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US08/037,327 Expired - Fee Related US5375464A (en) 1992-05-29 1993-03-26 Process for device for steering vehicle wheels rolling on test stands

Country Status (6)

Country Link
US (1) US5375464A (de)
EP (1) EP0577855B1 (de)
JP (1) JPH07270281A (de)
AT (1) ATE128767T1 (de)
DE (1) DE59203912D1 (de)
ES (1) ES2077920T3 (de)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5604296A (en) * 1994-07-27 1997-02-18 Nissan Motor Co., Ltd. Compliance tester
WO1998006590A2 (en) * 1996-08-15 1998-02-19 Mts Systems Corporation Low noise wheelpan
US5777220A (en) * 1995-11-21 1998-07-07 Pirelli Coordinamento Pneumatici S.P.A. Device for a braking and traction test of a wheel comprising a rim and a tire
US6050137A (en) * 1998-11-12 2000-04-18 Burke E. Porter Machinery Company Wheel restraint assembly
US6155110A (en) * 1997-04-24 2000-12-05 Bridgestone/Firestone, Inc. Method for predicting tire performance on rain groove roadways
US6612152B2 (en) * 1999-05-01 2003-09-02 James E. Keaton Lifting, servicing, and diagnosing automobiles
DE102006016764A1 (de) * 2006-04-10 2007-10-18 GM Global Technology Operations, Inc., Detroit Verfahren zum Prüfen eines Kraftfahrzeuglenksystems
US20090301183A1 (en) * 2008-06-09 2009-12-10 Mts Systems Corporation Flat belt roadway simulator with steer and/or camber adjustment and method for ascertaining rolling loss
CN102192842A (zh) * 2011-03-25 2011-09-21 唐光涛 车身底盘异响诊断仪
CN103487265A (zh) * 2013-10-08 2014-01-01 长安大学 汽车动力转向系统研发和性能检测平台
US10976216B2 (en) * 2019-08-27 2021-04-13 GM Global Technology Operations LLC Vehicle test apparatus

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09288047A (ja) * 1996-01-25 1997-11-04 Carl Schenck Ag 試験台上における走行車の拘束および舵取り方法とこの方法を実施するための装置
EP2166332B1 (de) * 2008-09-17 2015-01-07 Dürr Assembly Products GmbH Verfahren und Vorrichtung zur Spurführung eines Fahrzeugs
CN103439118A (zh) * 2013-08-08 2013-12-11 常州万安汽车部件科技有限公司 六通道车辆动态试验台
DE102016225924A1 (de) 2016-12-21 2018-06-21 Aip Gmbh & Co. Kg Vorrichtung zum Prüfen von Fahrzeugen
DE102018203296A1 (de) 2018-03-06 2019-09-12 Aip Gmbh & Co. Kg Vorrichtung zum Prüfen von Fahrzeugen
JPWO2021193054A1 (de) * 2020-03-27 2021-09-30
CN113865892B (zh) * 2021-09-01 2024-05-17 浙江航驱汽车科技有限公司 一种电动助力转向器整车与eolt台架换向噪声相关性分析方法
CN114778128A (zh) * 2022-03-31 2022-07-22 东风汽车集团股份有限公司 检测整车异响的全工况动态模拟试验台架及其试验方法

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US4912970A (en) * 1988-05-06 1990-04-03 Gicewicz Gerald P Diagnostic testing device

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JPS5279401A (en) * 1975-12-26 1977-07-04 Nissan Motor Co Ltd Steering device of test vehicle in bad road travelling test
DE3303588A1 (de) * 1982-02-03 1983-08-11 Volkswagenwerk Ag, 3180 Wolfsburg Einrichtung zur automatischen betaetigung von bedienungshebeln eines kraftfahrzeugs auf einem rollenpruefstand
DE3744631A1 (de) * 1987-12-31 1989-07-13 Friedrich Prof Dr Ing Klinger Verfahren und vorrichtung zur durchfuehrung von lebensdaueruntersuchungen an fahrzeugen

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4912970A (en) * 1988-05-06 1990-04-03 Gicewicz Gerald P Diagnostic testing device

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5604296A (en) * 1994-07-27 1997-02-18 Nissan Motor Co., Ltd. Compliance tester
US5777220A (en) * 1995-11-21 1998-07-07 Pirelli Coordinamento Pneumatici S.P.A. Device for a braking and traction test of a wheel comprising a rim and a tire
WO1998006590A2 (en) * 1996-08-15 1998-02-19 Mts Systems Corporation Low noise wheelpan
US5744708A (en) * 1996-08-15 1998-04-28 Mts Systems Corporation Wheelpan with damping structures
WO1998006590A3 (en) * 1996-08-15 1998-05-22 Mts System Corp Low noise wheelpan
GB2333078A (en) * 1996-08-15 1999-07-14 Mts System Corp Low noise wheelpan
GB2333078B (en) * 1996-08-15 2000-06-07 Mts System Corp Low noise wheelpan
US6155110A (en) * 1997-04-24 2000-12-05 Bridgestone/Firestone, Inc. Method for predicting tire performance on rain groove roadways
US6050137A (en) * 1998-11-12 2000-04-18 Burke E. Porter Machinery Company Wheel restraint assembly
US20040061100A1 (en) * 1999-05-01 2004-04-01 Keaton James E. Self-propelled crawler for lifting, servicing, and moving automobiles
US6612152B2 (en) * 1999-05-01 2003-09-02 James E. Keaton Lifting, servicing, and diagnosing automobiles
US6772997B2 (en) 1999-05-01 2004-08-10 James E. Keaton Self-propelled crawler for lifting, servicing, and moving automobiles
DE102006016764A1 (de) * 2006-04-10 2007-10-18 GM Global Technology Operations, Inc., Detroit Verfahren zum Prüfen eines Kraftfahrzeuglenksystems
DE102006016764B4 (de) * 2006-04-10 2009-04-30 GM Global Technology Operations, Inc., Detroit Verfahren zum Prüfen eines Kraftfahrzeuglenksystems
US20090301183A1 (en) * 2008-06-09 2009-12-10 Mts Systems Corporation Flat belt roadway simulator with steer and/or camber adjustment and method for ascertaining rolling loss
US7908916B2 (en) * 2008-06-09 2011-03-22 Mts Systems Corporation Flat belt roadway simulator with steer and/or camber adjustment and method for ascertaining rolling loss
CN102192842A (zh) * 2011-03-25 2011-09-21 唐光涛 车身底盘异响诊断仪
CN102192842B (zh) * 2011-03-25 2013-08-21 唐光涛 车身底盘异响诊断仪
CN103487265A (zh) * 2013-10-08 2014-01-01 长安大学 汽车动力转向系统研发和性能检测平台
CN103487265B (zh) * 2013-10-08 2016-01-20 长安大学 汽车动力转向系统研发和性能检测平台
US10976216B2 (en) * 2019-08-27 2021-04-13 GM Global Technology Operations LLC Vehicle test apparatus

Also Published As

Publication number Publication date
ES2077920T3 (es) 1995-12-01
EP0577855A1 (de) 1994-01-12
JPH07270281A (ja) 1995-10-20
EP0577855B1 (de) 1995-10-04
ATE128767T1 (de) 1995-10-15
DE59203912D1 (de) 1995-11-09

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